EP3318335B1 - Chaînes à rouleau pour cycle - Google Patents

Chaînes à rouleau pour cycle Download PDF

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Publication number
EP3318335B1
EP3318335B1 EP17001781.8A EP17001781A EP3318335B1 EP 3318335 B1 EP3318335 B1 EP 3318335B1 EP 17001781 A EP17001781 A EP 17001781A EP 3318335 B1 EP3318335 B1 EP 3318335B1
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EP
European Patent Office
Prior art keywords
chain
roller
plates
outer contour
link plates
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP17001781.8A
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German (de)
English (en)
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EP3318335A8 (fr
EP3318335A1 (fr
Inventor
Bruno Miguel Ferreira da Silva Ribeiro
Pedro Miguel Nunes Dos Santos
Diogo Daniel Soares da Silva
Matthias Reinbold
Henrik Braedt
John Collen
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SRAM Deutschland GmbH
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SRAM Deutschland GmbH
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Publication date
Priority claimed from DE102017009632.5A external-priority patent/DE102017009632A1/de
Application filed by SRAM Deutschland GmbH filed Critical SRAM Deutschland GmbH
Publication of EP3318335A1 publication Critical patent/EP3318335A1/fr
Publication of EP3318335A8 publication Critical patent/EP3318335A8/fr
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Publication of EP3318335B1 publication Critical patent/EP3318335B1/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16G—BELTS, CABLES, OR ROPES, PREDOMINANTLY USED FOR DRIVING PURPOSES; CHAINS; FITTINGS PREDOMINANTLY USED THEREFOR
    • F16G13/00—Chains
    • F16G13/02—Driving-chains
    • F16G13/06—Driving-chains with links connected by parallel driving-pins with or without rollers so called open links
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
    • B62M9/00—Transmissions characterised by use of an endless chain, belt, or the like
    • B62M9/04—Transmissions characterised by use of an endless chain, belt, or the like of changeable ratio
    • B62M9/06—Transmissions characterised by use of an endless chain, belt, or the like of changeable ratio using a single chain, belt, or the like
    • B62M9/10—Transmissions characterised by use of an endless chain, belt, or the like of changeable ratio using a single chain, belt, or the like involving different-sized wheels, e.g. rear sprocket chain wheels selectively engaged by the chain, belt, or the like
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
    • B62M9/00—Transmissions characterised by use of an endless chain, belt, or the like
    • B62M2009/005—Details of transmission chains specially adapted for bicycles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
    • B62M9/00—Transmissions characterised by use of an endless chain, belt, or the like
    • B62M9/04—Transmissions characterised by use of an endless chain, belt, or the like of changeable ratio
    • B62M9/06—Transmissions characterised by use of an endless chain, belt, or the like of changeable ratio using a single chain, belt, or the like
    • B62M9/10—Transmissions characterised by use of an endless chain, belt, or the like of changeable ratio using a single chain, belt, or the like involving different-sized wheels, e.g. rear sprocket chain wheels selectively engaged by the chain, belt, or the like
    • B62M9/12—Transmissions characterised by use of an endless chain, belt, or the like of changeable ratio using a single chain, belt, or the like involving different-sized wheels, e.g. rear sprocket chain wheels selectively engaged by the chain, belt, or the like the chain, belt, or the like being laterally shiftable, e.g. using a rear derailleur

Definitions

  • the present invention relates to a roller chain for bicycles that is asymmetrically designed with respect to the longitudinal axis.
  • Roller chains as drive chains for bicycles with derailleur gears from the prior art are composed of chain links that are arranged so that they can pivot relative to one another, with the help of which a closed chain ring is formed for the transmission of driving force.
  • a chain link mainly consists of a pair of inner plates or outer plates.
  • the tabs each have two end areas with a round outer contour, which are connected by a connecting area with a usually tapered outer contour. In the end areas there are holes concentric to the outer contour.
  • Alternating inner link and outer link chain links are rotatably connected to each other at the chain joints using chain bolts.
  • the perforations are located concentrically to the outer contours of the round end areas of the tabs.
  • the chain pins are pressed into the holes in the outer plates, while there is play between the holes in the inner plates and the chain pins to ensure rotational mobility.
  • the aim is to make the distances between the tabs as large as possible in the direction perpendicular to the inner surface of the tabs.
  • catch chamfers serve to create an inlet funnel for the sprocket teeth entering the space between the plates.
  • the invention uses, in addition to the advantages of asymmetrical chain plates, the retention of the loaded cross-sections. This means that the increase in loads that occurs due to a reduction in dimensions in one direction is compensated for by increasing the dimensions in other directions.
  • Asymmetry is about asymmetry with respect to the longitudinal axis or longitudinal plane through the two geometric axes of the two chain bolts on each chain link.
  • such asymmetrical chain plates have other effects, such as improving the guidance of the chain when engaging on the front or rear sprocket.
  • roller chains for bicycles have already been exploited in roller chains for bicycles.
  • inventive roller chain further features relating to the outer contour of the chain plates are added, and further effects are sought, such as improved guidance of the chain on the sprockets in accordance with good behavior of the chain when passing through teeth on the sprocket when shifting to the adjacent sprocket.
  • Another case is a rotation of the chain strand about an axis perpendicular to the plane through the geometric axes of the chain bolts by 180 degrees, which is also associated with an exchange of the two longitudinal rows of alternating inner and outer plates. Then there is no change if, with the same viewing direction from above, there are asymmetrically arranged shaped elements on both the front left and rear right of the pull section of the chain mounted on the bicycle.
  • the roller chain on bicycles interacts with the teeth on sprockets. These sprockets are front sprockets on the pedal crank and rear sprockets on the rear wheel of the bicycle.
  • the roller chain is usually formed by connecting the two ends together to form a chain ring, which has a chain ring inside and a chain ring outside, and which extends essentially along a central plane. Due to the very limited mobility of the chain links perpendicularly relative to the central plane, when the ends of the original chain piece are connected, it is determined what becomes the inside of the chain ring and what becomes the outside of the chain ring. Only the inside of the chain ring interacts with the teeth on the chain wheels mentioned.
  • the upper chain guide rollers on rear deraille alone interact with the outside of the chain ring.
  • the outer contour of the tabs facing the inside of the chain ring is adopted from conventional chains.
  • the inner and outer plates of conventional chains are stamped from sheet metal as raw material. They each have a pair of end regions and a connection region that connects the pair of end regions. The end areas are larger in the direction of the plane of the raw material than in the connection areas. This leads to balanced load conditions in the present design.
  • the main load on the chain plates arises from the chain pulling force in the longitudinal direction of the plates.
  • torsional forces around the longitudinal direction of the chain strand are also important, which arise primarily when if the chain is shifted between the sprockets during the switching process and the chain pulling force is not reduced, ie if the cyclist continues to pedal with great force during the switching process.
  • the contour of the chain plates of the chain according to the invention on the outside of the chain ring is selected so that the distance between the longitudinal plane through the geometric axis of the chain bolts and the contour is significantly larger than with conventional chains. A noticeable effect occurs when this distance is increased by half the radius of the holes in the tabs.
  • the contour line is chosen as a tangent to the outer curves of the two end regions of the tab.
  • Different contour lines are possible, for example as circular arcs on the outer curves of the two end areas.
  • Inner chain plates with an outer contour shape that is asymmetrical relative to the longitudinal plane or longitudinal axis are known per se, for example from the patent documents GB1595091 ; US 4596539 , FR 812827 , EP 0236184 , DE 2829424 .
  • the aim of such solutions is to create space for passage past a tooth during the switching process. This will be the case
  • Outer contour of chain plates on the plate contour on the inside of the chain ring is approximated far in the direction of the longitudinal axis of the plates compared to conventional chains. This increases the loads on the chain considerably, because large bending moments caused by the chain tension now occur in the chain link, which are reflected in the link contour on the inside of the chain ring as additional tensile stresses.
  • the difference to an outer plate chain link in the locking link shown is that the chain bolts are not pressed into holes in the plates at their end. Instead, elongated holes essentially aligned in the longitudinal direction of the tabs are provided for the positive reception of the ends of the closure member bolts.
  • a constriction at one end of the bolt is moved along an elongated hole until this constriction releasably engages at the end of the elongated hole.
  • the outer contour of the tab of the closure link is based on the shape of the elongated hole, with the side of the closure link intended for the inside of the chain ring having an outer contour which corresponds to the outer contour of a conventional chain link. This prevents the locking link from interacting with the teeth of the sprockets to behave differently than an outer plate chain link.
  • a first aspect of the concept according to the invention consists in maintaining or increasing the cross-sectional area of the tabs in the connection area. This applies at least to the inner plates, where it is important to have the largest possible clear width between the connecting area of the pair of these inner plates in order to achieve favorable conditions for the engagement of the teeth on the sprockets, and possibly also the outer plates.
  • the most noticeable change compared to conventional chains is that the originally tapered connection area of the straps is enlarged in the direction of the extension plane of the strap.
  • the load capacity of the chain can be increased, which is desirable, for example, in electric drives for bicycles because the loads resulting from the rider's pedaling movement and the electric drive add up.
  • Inner chain plates made of a material with a smaller material thickness are known from the GB1595091 , but there is no indication that anything should be done about the reduced strength due to the reduced material thickness.
  • the inner flaps in this document also do not have any collars for which material to be formed must be available. Rather, bushings on which the chain rollers are mounted are inserted into the holes in the inner plates.
  • the collars on the side of the inner tabs facing the opposite inner tab are formed by reshaping the blank that was originally punched out of a flat strip material. It goes without saying that for this forming process, which is similar to a deep-drawing process, appropriate material must also be available from which the tubular collar then, so to speak, "grows out" of the flat blank.
  • the material thickness in the connection area and at the end areas as well as the material thickness of the blank punched out of a strip material can be selected.
  • the material thickness of the blank cannot be reduced arbitrarily in order to obtain a narrow chain in a direction parallel to the chain pins.
  • a reduction in the material thickness of the band material used is limited by the necessary load capacity of the chain link and by the manufacturing conditions mentioned for the collars.
  • the inside of the inner flap can be provided with a recess in the connection area, which has the effect of reducing the material thickness in this area. This causes the distance in the direction parallel to the chain bolts between the connecting areas and thus the space between the plates to become larger. If there is an inner tab projection in addition to the recess, then the distance between the end regions of the inner tab is smaller than the distance between the connecting area of the inner tab. It may then no longer be possible for the tooth tip to engage properly between the inner plate ends that protrude radially over the chain roller.
  • the chain In the drive case with the interaction of the roller chain with the sprocket, the chain is functioning properly if the sequence of tooth tips entering the space between the plates one after the other repeatedly aligns the chain links so that they are aligned with the center plane of the sprocket. This is especially the case when the chain is skewed, i.e. H. This is not unproblematic when the chain runs diagonally onto the sprocket.
  • the chain In the case of switching gears from a smaller to a larger sprocket, the chain should ultimately also have a first tooth tip after the chain links have been displaced in a direction parallel to the chain bolts towards the larger sprocket as a result of the action of a chain guide device from a front derailleur or from a rear derailleur larger sprocket enter the space between the plates.
  • an inner plate link it is the inner plates and the chain rollers that define the space for the teeth of the sprockets to enter and engage. Contact between the tooth and the inner chain plate can occur right at the beginning of the engagement process. Chamfers on the inside of the tab increase the space available for the tooth and make it easier to engage.
  • the space between the plates is defined by the chain rollers, the insides of the outer plates and the components of the inner plates that protrude beyond the chain rollers if there is an inner plate projection.
  • This effect increases in the drive case as the chain skew increases, i.e. H. the more the rear sprocket (pinion) is offset from the plane of the front sprocket in a direction perpendicular to this plane.
  • the outer periphery of the inner link can come into disruptive contact with the flank of the tooth, which is located in the space between the teeth, which puts the chain link in an undesirable position.
  • An inner plate protrusion has a negative effect, for example when switching from a larger to a smaller rear sprocket. Then, at the beginning of the switching process, the chain is displaced relative to the sprocket tooth in a direction parallel to the chain bolts and the tip of the pinion tooth still has to engage in the space between the outer plates.
  • the chain guide devices on a front derailleur and a rear derailleur prevent the chain from coming off.
  • a front chain thrower, and correspondingly a front chain guide device has been omitted from those roller chain drives that have been successfully introduced into bicycles in the recent past. This step was made possible with sprockets that have thickened teeth that well fill the space between the plates on the outer plate links. This also achieves optimized guidance of the chain on the sprocket on outer link chain links, which in conventional chain drives only occurs between the sprocket tooth and the inner link link.
  • the effect of an inner flap projection varies depending on the position at which the outer contour of the end region of the inner flap has the inner flap projection.
  • An inner plate projection can be present in the area of the outer contour of the inner plates, which is approximately parallel to the longitudinal axis and thus in the transverse direction of the chain (transverse projection).
  • the sections with such a transverse projection only approach the tooth contour in the tooth gap at the end of the chain link pivoting and thus later.
  • a transverse projection has at least an effect in terms of guiding the chain when pivoting in at the end of the pivoting movement of the chain link and in fixing the chain links engaged on the chain wheel.
  • a crossover has little effect on the process of shifting the chain for gear shifting.
  • a longitudinal overhang also has an effect on the maximum possible chain skew, at which the chain just barely engages cleanly with the teeth on the sprocket.
  • Chain skew inevitably occurs on roller chain drives for bicycles with several rear sprockets (sprockets) as a result of the non-aligned front and rear sprockets, which are involved in the power transmission through the chain in the drive case.
  • the cases of the smallest front sprocket in combination with the largest rear sprocket as well as the largest front sprocket in combination with the smallest rear Sprockets are the most critical and are therefore usually not recommended by the manufacturers of bicycle drive components. Bicycle users are advised not to use these combinations in practical use.
  • an inner plate projection contributes to guiding the chain on the sprockets.
  • the inner plate protrusion is more or less annoying when it is important to shift the chain properly for the purpose of changing gears.
  • a special application is on a racing bike, where it is still appreciated that a large gear jump can be achieved by switching to the adjacent front sprocket once.
  • a completely omitted longitudinal projection i.e. a projection of the inner plate relative to the chain roller near the longitudinal axis of the inner plate, is possible because the devices for transferring the chain between different chain wheels already have separate chain guide devices. This improves the skew properties because the tooth entering the space between the plates does not collide with the longitudinal projection.
  • there is no chain guide device for a front derailleur as this derailleur is completely omitted.
  • the inner plate projection is then also used as a chain guide.
  • the bevels and chamfers on the inner plate projection on the inner plates are provided so that the teeth on the sprockets and the chain engage well. They go far beyond what is already known as a bevel at an angle of 45 degrees for breaking a sharp edge on a solid part or on a sheet metal part such as a chain link. They form funnel-shaped “passages” on the chain for the tooth tips to enter and exit.
  • the inner plate projection is divided into longitudinal projection and transverse projection, as already discussed.
  • the longitudinal projection and transverse projection are used in configurations that differ from one another. On the one hand, this is due to the fact that the longitudinal and transverse projections have different effects on wear. On the other hand, under certain conditions, the longitudinal projection and its guiding function can be dispensed with, or the longitudinal projection is reduced.
  • this problem is solved in that the inner tab is provided without a longitudinal projection but with a transverse projection if the guiding function of the longitudinal projection can be dispensed with. This is the case with chains that are used in drive systems with sufficient other guide elements, such as chain guide devices on both front derailleurs and rear derailleurs.
  • the management function is desired there and can also be used. Accordingly, a different bevel angle can be selected on the transverse projection.
  • the bevels on the longitudinal projection on the one hand and on the transverse projection on the other hand can have different bevel angles, the angle between the chamfer and the plane formed by the inside of the inner tab.
  • the bevel angle on the longitudinal projection is preferably larger than that on the transverse projection.
  • the tab has a bevel angle of approximately 38 degrees at the longitudinal projection and a bevel angle of approximately 51 degrees at the transverse projection.
  • the asymmetrical outer contour of the chain link allows the chain links to be particularly thin.
  • the strength of the chain plate is maintained despite the low material thickness because the cross section, although it decreases in the axial direction (thickness), is increased in the transverse direction due to the asymmetrical shape of the plates and therefore remains approximately the same overall.
  • a particularly low material thickness of the chain plates in a range of approximately 0.65 mm to 0.75 mm is aimed for.
  • the inner tab preferably has a material thickness of 0.70 mm.
  • the material thickness of the inner tabs can vary Connection area can be further reduced by a recess.
  • the increase in cross-section due to the asymmetrical shape of the inner tab in the connection area contributes particularly strongly to the strength of the tab.
  • This recess creates space for the meshing teeth of the pinions - the space between the plates in a pair of plates is increased.
  • the material thickness in the connection area of the tab is then in a range of 0.55 mm to 0.65 mm.
  • the material thickness in the area of the recess is particularly preferably 0.60 mm.
  • the outer tab can also have such a recess in the connection area.
  • the connecting sections of the chain plates must have appropriately formed elements that protrude into the space between the plates and narrow it in a wedge shape towards the outer contour of the plate.
  • comparable elements for interacting with the teeth are already well known, but these elements have so far only been effective on the path of the tooth tip from the outer contour of the chain link to the longitudinal axis of the chain link. Now there is an interaction with the tip of the tooth after it has passed the longitudinal axis of the chain link and moved into the space beyond the longitudinal axis.
  • the chain guide parts which are differentiated in terms of their radial position on the sprocket, are selectively connected to the for their intended partners come into interaction.
  • the further outer chain plates extend further radially inwards on the sprocket, after they have passed the chain guide parts for the inner plates, which are arranged further radially outward, without there being an interaction with them.
  • an annular bead concentric to the axis of rotation of the sprocket can be provided, which is easy to manufacture.
  • Narrow chains are particularly important for multiple sprocket arrangements with an increased number of eleven, twelve, thirteen or more sprockets. Due to the limited installation space in the axial direction, the pinions must be positioned at very short distances from one another. The strand of inner and outer plates arranged alternately on one side of the chain must be so narrow that it fits into the free spaces between the sprockets without colliding with the next smaller or next larger sprocket.
  • the largest two sprockets in particular can have teeth of different thicknesses in the axial direction, which have a positive effect on the chain guidance. The thickening of the teeth is advantageously formed on the side of the pinion that faces the adjacent larger pinion.
  • the teeth are not thickened; otherwise, when the chain engages with a sprocket, there would be contact and thus a disturbing noise development between the chain and the teeth on the adjacent larger sprocket.
  • the thickening on the thick teeth is so large that a thick tooth fits into the space between the tabs of an outer link link, but not into the smaller space between the tabs of an inner link link.
  • the pinions preferably have an even number of teeth, with thick and thin teeth alternating along the circumference.
  • the chain according to the invention engages with a multiple sprocket arrangement arranged on the rear wheel of a bicycle and with a front chainring arrangement on a bottom bracket with one, two or three chainrings.
  • a multiple sprocket arrangement arranged on the rear wheel of a bicycle and with a front chainring arrangement on a bottom bracket with one, two or three chainrings.
  • the chain guidance on the front chainring can also be improved by using alternating thick and thin teeth.
  • the chain according to the invention is particularly narrow.
  • the asymmetrical tabs allow a very small tab thickness while maintaining strength.
  • the equalization of the material cross-section in the connection area of the tabs leads to an approximately constant tensile strength of the tabs.
  • the strength of the tabs in the ring area can be maintained with reduced tab thickness if the diameters of the end areas are also increased.
  • the material cross section of a thinner tab can also be compensated for at the end areas. With a constant diameter of the perforation and an increased diameter of the end regions, the ring spacing also increases, which further increases the tensile strength of the tab.
  • particularly narrow chain rollers with an increased chain roller diameter can also be used, which also help to reduce the overall width of the chain.
  • the increased chain roller diameter helps to reduce the surface pressure between the chain roller and the load flank of the tooth.
  • the increased chain roller diameter leads to an increased contact surface between the chain roller and the load flank of the tooth and thus compensates for the reduced chain roller width.
  • an increased chain roller diameter together with an increased diameter of the end regions of the inner plates allows a constant transverse projection of the inner plate beyond the chain roller.
  • the measures mentioned to reduce the overall chain width can be used separately or in combination.
  • a particularly narrow, stable and wear-resistant chain is achieved when the measures are combined.
  • a design concept with increasing the diameter of the chain roller in combination with reducing the axial length of this chain pin in connection with increasing the number of an arrangement of an ever larger number of sprockets on a multiple sprocket arrangement is coherent.
  • the axial distance between the pinions is smaller. This means that when the chain is moved from one pinion to the adjacent pinion, the bending angle of the chain becomes smaller, and with this reduced bending angle, the need for a tooth gap that is extended in the circumferential direction is also reduced. There is therefore still enough space for a tooth in the space between two chain rollers adjacent in the longitudinal direction of the chain.
  • the overall length of the tabs can be maintained because the cross sections along the longitudinal plane are not critical to existing stresses. This means that there is a reduction in the cross section as a result of the reduction in the material thickness without any loss of safety against breakage possible. This means that the distance between the outer periphery of the chain plates in the direction of the longitudinal plane is smaller than the second distance between the outer periphery of the chain plates in the direction of the transverse plane or in a direction 45 degrees between the longitudinal and transverse planes.
  • maintaining the overall length of the chain plates also plays a role in production, i.e. when punching out the chain plates from a strip material. If this total length is maintained, then the advantageous aspect is that the same length of band material is used per chain link. In addition, the feed of the strip material remains the same from one punching operation to the next punching operation, which is an advantage.
  • a chain ring is formed by connecting the two ends of a piece of chain together by suitable means, for example by a pair of I-shaped chain links.
  • This chain ring has an inside and an outside. Due to the rigidity of the chain piece in terms of torsion around the longitudinal axis of the plates as well as in terms of bending relative to a plane perpendicular to the chain pins, it is impossible to convert the inside to the outside and vice versa. With the creation of the chain ring, the inside and outside of the chain ring are clearly defined. In the case of the roller chain according to the invention, it is helpful that the chain sides provided as the inside or outside of the chain ring can also be easily distinguished from one another due to their asymmetrical shape.
  • One aspect of the invention is the clear distinction between a guide side of the chain links or chain plates on the outside of the chain ring on the one hand and the engagement side of the chain links or chain plates on the inside of the chain ring.
  • the guide side of the chain is optimized for guidance on the guide teeth of the upper chain guide roller on the chain guide of a rear derailleur.
  • the engagement side of the chain is designed for engagement with the front and rear sprockets (front chain rings and rear sprockets, respectively) of a bicycle and for switching between these sprockets.
  • the roller chain according to the invention inevitably leads to deviations compared to a previously symmetrically designed chain.
  • a chain that is already asymmetrically designed for reasons of strength can also be additionally optimized in terms of its design as an engagement and guiding side.
  • the connection area with a concave outer periphery is suitable as an engagement side because of the requirements for the required engagement properties.
  • Guide bevels on the guide side of the chain basically work in a similar way to catch bevels on the engaging side of the chain plates. They form a kind of "inlet funnel" for the guide teeth on the chain guide roller, which are shorter in the radial direction than teeth on sprockets.
  • gaps between the tabs can be narrowed, as in the US 4,741,725 has already been carried out with the narrowing of the space between the tabs between a pair of outer tabs.
  • the chain can split open if, when there is a large tensile force in the chain, the tip of a tooth on the sprocket penetrates into a gap between the chain roller and the inner plate or between the inner plate and the outer plate.
  • This large tensile force occurs when the chain links enter the tensile strand of the chain, which is under a large driving force. Then it happens that the outer link is separated from the chain pin.
  • Chamfers at the contact point between the inner and outer plate expand the existing gap and thus promote the possibility for the tip of the tooth to penetrate into the gap. Accordingly, there are limits as to how far chamfers on the outer periphery of the tabs can extend in order to avoid damaging splitting.
  • the length of the gap can increase or decrease depending on the bending angle over a length that cannot be neglected.
  • Deflecting chamfers on the outside of the inner plate also serve to allow good lateral passage of the chain plate on the side of the sprocket tooth. This case occurs, for example, when the chain is transferred from the larger sprocket to the adjacent smaller sprocket.
  • a guide chamfer has a smaller extent from the outer contour of the chain link in the direction perpendicular to the outer contour. Since a guide tooth on a chain guide roller enters the space between the plates in this direction, the length of a guide tooth on a chain guide roller corresponds. The length in the radial direction of a tooth on a sprocket is greater.
  • the guide side of an outer plate can now be designed in such a way that contact takes place between the guide side of the outer plate and the chain guide roller. This can be done by changing the external shape of the outer flap and by bending, as in the US 4,741,725 shown.
  • a deflecting chamfer on the guide side of the outer tabs is not necessary due to the inherent assignment of the deflecting function to the engagement side.
  • Transitions between different bevels can be freely designed, also with the aim of simple production.
  • a chain link (1, 2) consists primarily of a pair of inner plates (4) or outer plates (3).
  • the tabs (3, 4) each have two end regions (5) with a round outer contour (19), which are connected by a connecting region (6) with a usually tapered outer contour (17, 18). Perforations (7) are provided in the end regions (5) concentrically to the round outer contour (19).
  • the alternately arranged inner link links (2) and outer link links (1) are rotatably connected to one another at the chain joints (23) by means of chain bolts (12).
  • the chain pins (12) are pressed into the holes (7) in the outer plates (3), while there is play between the holes (7) in the inner plates (4) and the chain pins (12) to ensure the rotational mobility between the Chain links (1, 2).
  • the inner plates (4) each have collars (13) on their inner surface (8), with a chain roller (11) being rotatably arranged on a pair of collars (13) arranged in mirror images of one another.
  • the term “inner surface” refers to the surface of the inner tab (4), which faces another inner tab (4) and together with this forms a tab space (24).
  • the inner surfaces (8) of a pair of outer tabs (3) also form a tab space (24).
  • the outer surfaces (9) of the tabs (3, 4) point away from the tab space (24), which are in the Figures 2 and 9 is clearly visible.
  • a first edge distance (28) in the inner plates (4) of conventional chains is as large as the ring distance (27), which is the radial thickness of the rings around the perforations (7) in the end regions (5) of the inner plate (4). represents. This means that cross-sections of comparable size are available both in the connection area and in the two components around the perforation for the resulting tensile loads.
  • the first edge distance (28) is determined, namely as the distance between the outer contour (17 or 18) of the inner tab (4) and the longitudinal plane (20).
  • the ring distance (27) is to be determined between the edge of the perforation (7) and the convex outer contour (19) of the relevant end region (5).
  • the first edge distance (28) and the ring distance (27) must be determined for outer plates (3) in the same way as in the exemplary illustration in Figure 5 , which shows the inner tab (4).
  • Figure 12 the conditions in the roller chain according to the invention are shown using the example of the inner link. These conditions also apply to the outer tab of the embodiment, which is shown in the Figures 13 and 14 is shown in detail.
  • a closed chain ring as in Fig. 16 shown, is formed by means of two locking links in an L shape or in another way from a piece of chain.
  • an outer contour of the chain in the connection area inevitably comes to the inside of the chain ring.
  • this should be the first outer contour (17) which has a concave course.
  • the first edge distance (28) corresponds to the ring distance (27) and is therefore adopted from conventional chains. This means that the contact conditions between the chain according to the invention and the teeth on the front chain wheel, on the rear chain wheel and on the lower chain agitator wheel on the rear derailleur are taken over by conventional symmetrical chains.
  • the second outer contour (18) lies opposite the first outer contour (17) on the tab.
  • the second outer contour (18) is a straight line that runs tangentially to the two round outer contours (19) of the two end regions (5).
  • the second edge distance (30) is determined between the longitudinal axis (20) and the second outer contour (18). It is as large as the sum of the hole radius (29) and ring spacing (27) and is therefore significantly larger than the first edge spacing (28).
  • the course of the second outer contour (18) can also be concave or convex.
  • the one for the outer tab (3) in the Figures 13 and 14 The course of the second outer contour (18) shown is concave.
  • Repelling chamfers are shown on the outer surfaces (9) of the outer tabs (3).
  • Such deflector bevels (15) are known from the prior art, according to the illustrations in the Figures 1, 2 and 7 . They serve to allow the outer plate (3) that comes into contact with a tooth on the sprocket to slide off the tooth.
  • the deflector chamfers (15) prevent the chain from unintentionally riding on a tooth, which can lead to incorrect engagement of the chain on the sprocket and chain shedding.
  • the inner plate (4) can protrude in the radial direction relative to the chain roller. Accordingly, there is an inner tab projection, which can be divided into a longitudinal projection (25) and a transverse projection (26), as in the Figures 1 and 2 shown.
  • the longitudinal projection contributes to guiding the chain on the teeth of the sprocket, but on the other hand, it can be disruptive during switching operations, e.g. B. when transferring the chain from the larger to the smaller rear sprocket.
  • the transverse projection (26) is primarily effective for holding the Chain on the teeth of the sprocket when the chain and teeth are fully meshed with each other. This can help ensure that the chain links only move slightly in a direction perpendicular to the plane of the sprocket and their transverse mobility is therefore restricted.
  • a transverse projection (26) is used, while a longitudinal projection (25) is omitted.
  • the transverse projection (26) is pointed out.
  • Fig. 9 There is no evidence of a longitudinal projection (25) in the corners of the tab spaces (24). Rather, the chain roller (11) protrudes slightly from the inner plate (4).
  • the transverse projection (26) has a bevel angle (35) of approximately 49 degrees.
  • the dimensioning of the bevel angle is related to: Figure 15 discussed in more detail.
  • Fig. 9 It is clearly visible that the gaps between the tabs (24) are enlarged by the additional recesses (33) in the connecting areas (6) of the inner and outer tabs (4, 3).
  • very narrow chains such as the chain according to the invention with very narrow chain rollers (11)
  • the space between the plates (24) of the inner plate links (2) is particularly narrow.
  • the recesses (33) on the inner surfaces (8) in the connecting areas (6) of the inner plates (4) still create enough space for the pinion teeth to engage.
  • the additional catching chamfers (16) along the first and second outer contours (17, 18) also make it easier to catch the pinion teeth.
  • the transition from the recess (33) to the catch bevel (16) is particularly preferably tangential, ie without edges. This supports a particularly soft and low-noise sliding of the pinion teeth into the spaces between the tabs (24).
  • the recesses (33) can be arranged both on the inner surfaces (8) of the inner plates (4) and on the outer plates (3).
  • the recesses (33) are preferably formed by material deformation, for. B. pressing or by material removal e.g. B. Milling produced.
  • the outer surface (9) of the tab remains flat so that it does not collide with a pinion when shifting.
  • the asymmetrical shape and the associated increased cross-section of the inventive chain link contribute significantly to the fact that the link is stable enough and can withstand the forces to be transmitted despite the reduced material thickness in the area of the recess.
  • Fig. 10 shows the inner link of the chain 8 and 9 in a perspective view, viewed from the inner surface of the tab.
  • the recess (33) ie the lowering of the connection area (6) compared to the two end areas (5), is clearly visible.
  • a catch chamfer (16) adjoins the recess (33) when viewed in the transverse direction.
  • the catch chamfer (16) on the first outer contour (17) is of particular importance because it lies on the inside of the closed chain ring and is brought into engagement with the teeth of the rear and front sprockets.
  • the material thickness in the area of the recess (33) is approximately 0.6 mm.
  • the remaining material thickness of the inner flap is otherwise approximately 0.7 mm.
  • the recess (33) is therefore approximately 0.1 mm deep.
  • Fig. 11 shows the inner link of the chain 8 and 9 in a perspective view, viewed from the outer surface of the tab.
  • the outer surface is preferably flat.
  • Fig. 15 shows the conditions on the chamfer (34) on the round outer contour (19) at an end region (5).
  • the bevel (34) forms an inner bevel edge (37) with the inner surface (8) and an outer bevel edge (38) with the round outer contour (19).
  • the bevel depth (36) is measured in a direction parallel to the hole axis (14) between the inner bevel edge (37) and the outer bevel edge (38).
  • the bevel angle (35) is determined in a plane radial to the hole axis (14) between the plane of the inner surface (8) and the surface of the bevel (34). It has proven to be advantageous for certain conditions if the bevel angle (35) in the area of the inner tab projection (25, 26) is small.
  • the inner bevel edge (37) is radially further inward than the outer edges of the chain roller (11). This ensures that a tooth of a chain wheel entering the space between the plates (24) finds the widest possible "inlet funnel” which is formed by the surfaces of the chamfers on the two inner plates (4) of a pair of plates. The tip of the tooth can then slide unhindered radially inwards on the chamfer (34).
  • Fig. 16 It can be seen how, using two L-shaped locking links, a piece of chain is formed into a closed chain ring for driving force transmission, which has an inside and an outside.
  • Figure 17 shows an asymmetrical chain 8 and 9 in engagement on a rear set of sprockets in a perspective view and Figure 18 in a top view.
  • the schematic representations show only part of the drive train, which usually includes a closed chain ring that passes through a rear derailleur with two chain guide rollers and engages in a front chainring arrangement.
  • the front chainring assembly typically includes one, two or three chainrings. If there are a large number of rear sprockets, one or two front chainrings are sufficient.
  • Narrow chains are particularly important for multiple sprocket arrangements (40) with an increased number of eleven, twelve, thirteen or more sprockets (41). Due to the small installation space in the axial direction, the pinions (41) must be positioned at very short distances from one another.
  • the pinion arrangement (40) shown comprises exactly twelve pinions (41), which are positioned at predetermined distances from one another.
  • the smaller sprockets, especially the smallest are six sprockets in a slightly larger one Spaced apart from each other than the larger pinions, especially the largest six pinions.
  • An annular bead (45) is also arranged on the smallest pinion (41), which pushes the chain outwards in the axial direction and thus reduces the risk of chain skew.
  • the chain shown engages in the teeth (42) of the third largest sprocket (41) of the multiple sprocket arrangement (40).
  • the chain must be so narrow that it fits into the spaces between the sprockets (41) without colliding with the next smaller or next larger sprocket.
  • the deflecting chamfers and catching chamfers on the outer and inner surfaces of the plates interact with the chamfers (43) of the teeth (42) of the pinions (41) when switching from one pinion to the next.
  • the pinions (41) have switching features (44) that enable switching.
  • the largest two pinions (41) in particular can have teeth (42) of different thicknesses in the axial direction, which have a positive effect on the chain guidance.
  • the thickening of the teeth (42) is preferably formed on the back of the pinion and is not visible here.
  • the thickening on the thick teeth is dimensioned such that a thick tooth fits into the space between the tabs (24) of an outer link (1), but not into the smaller space (24) of an inner link (2).
  • thick and thin teeth may alternate along the circumference.
  • the indicated chain engages with the multiple sprocket arrangement (40) shown and a front chainring arrangement with two chainrings, not shown here.
  • the chain guidance on the front chainring can also be improved by using alternating thick and thin teeth.
  • the chain according to the invention is particularly narrow.
  • the asymmetrical tabs (3, 4) allow a very small tab thickness - the compensation of the material cross-section in the connection area of the tabs leads to an approximately constant tensile strength of the tabs.
  • the tensile strength of the tabs (3, 4) can be increased additionally if the diameter of the end regions (5) are also increased.
  • the material cut of a thinner tab can also be compensated for at the end areas (5).
  • the ring spacing (27) also increases, which further increases the tensile strength of the tab - compare here Figure 12 .
  • narrow chain rollers (11) with an increased chain roller diameter can also be used, which also help to reduce the overall width of the chain.
  • the increased chain roller diameter helps to reduce the surface pressure between the chain roller and the load flank of the tooth.
  • the increased chain roller diameter leads to an increased contact surface between the chain roller and the load flank of the tooth and thus compensates for the reduced chain roller width.
  • an increased chain roller diameter together with an increased diameter of the end regions (5) of the inner plates (4), allows a constant transverse projection (26) of the inner plate (4) beyond the chain roller (11) - see also Figure 8 .
  • the measures mentioned to reduce the overall chain width can be used separately or in combination.
  • a particularly narrow, stable and wear-resistant chain is achieved when the measures are combined.
  • the second embodiment of an inner tab (4) according to the invention is in the Figures 19 and 20 in a perspective view and in the Figure 21 shown in a view looking perpendicular to the outer surface (9) (or parallel to the perforation axes (14)).
  • Essential features are of the embodiment according to Figures 8 to 15 been taken over.
  • the second embodiment is implemented more consistently than the embodiment according to Figures 8 to 15 the principles of arranging only guide bevels (53) on the guide side (51) of the chain, but no catch bevels (16) and no rejection bevels (15).
  • the inner tab (4) has two round end areas (5), which are connected by the connecting area (6).
  • the second outer contour (18) has a straight course and merges tangentially into the outer contour at the two round end regions (5).
  • Essentially concentric to the round outer contour (19) There are holes (7) in the round end areas (5).
  • Each of the perforation axes (14) is also the axis of a hollow cylindrical collar (13) on the inner surface (8) of the inner tab (4).
  • the material thickness of the inner plates (4) in the two embodiments of the chain according to the invention according to Figures 8 to 18 and 19 to 23 is 0.73 millimeters, as opposed to 0.77 millimeters for a burdock according to the Figures 1 to 7 .
  • a step (55) is formed between the inner surface (8) around a collar (13) and the inner surface (8) at the connecting area (6) due to the recess (33). This step (55) is concentric to the hole axis (14).
  • the second outer contour (18) on the inner plate (4) corresponds to the guide side (51) of the chain joined to a chain ring.
  • the guide chamfer (53) is a guide chamfer (53) on the second outer contour (18) between the inner surface (8) on the connecting area (6) and the round outer contour (19) on both end areas (5) for interaction with the chain guide roller of a rear derailleur.
  • the guide chamfer (53) also has a straight course and merges at both ends into the chamfer (34) on the round outer contour (19).
  • the first outer contour (17) on the inner plate (4) corresponds to the engagement side (50) of the chain joined to form a chain ring. Accordingly, there is a catch chamfer (16) on the first outer contour (17) between the inner surface (8) at the connecting area (6) and the round outer contour (19) at both end areas (5). to interact with a tooth on a pinion. Corresponding to the arcuate shape of the first outer contour (17), the catch bevel (16) also has an arcuate shape. The catching bevel (16) merges at both ends first into a transition surface and then into the bevel (34) on the round outer contour (19).
  • transition surface corresponds to the attempt to create the smoothest possible transition and also to avoid a noticeable gap between the inner plate (4) and the chain rollers (11) which are rotatably mounted on the collar (13) when the chain is installed ).
  • a gap at this point would possibly allow the tip of a sprocket tooth to penetrate, with the risk of the chain splitting open.
  • the diameter of the chain roller (11) in the two embodiments of the chain according to the invention according to Figures 8 to 18 and 19 to 23 is 7.9 millimeters, as opposed to 7.7 millimeters for a burr according to the Figures 1 to 7 .
  • the width of the chain roller (11) in the two embodiments of the chain according to the invention according to Figures 8 to 18 as well as 19 to 23 is 1.85 millimeters, as opposed to 1.7 millimeters for a burdock according to the Figures 1 to 7 .
  • the bevel (34) has a variable bevel angle (35) along its course on the round outer contour (19). This takes into account the different requirements for the longitudinal projection (25) compared to the transverse projection (26), as detailed in connection with Fig. 15 is described.
  • the portion of the inner surface (8) that protrudes from the chain roller (not shown) without a chamfer is wider in the radial direction than on the longitudinal projection (25). This means that the transverse projection has a particularly good centering effect on the pinion tooth when a pinion tooth enters the space between the tabs.
  • the longitudinal projection (25) with the chamfer (34), or at least this chamfer (34) alone, would not have to extend so far in the direction of the longitudinal axis (20), but could be shorter because the contact with a guide tooth on one Chain guide roller could no longer take place there anyway. Accordingly, the extension of the chamfer (34) on the longitudinal projection would then be extended on the guide side up to the longitudinal axis (20) and possibly beyond the longitudinal axis (20). This could be designed so that the in Fig. 21 Longitudinal projection (25) arranged on both sides of the longitudinal axis (20) without a chamfer (34) would be displaced to the guide side (51).
  • the second outer contour (18) has a straight course and merges tangentially into the round outer contour (19) at the two round end regions (5).
  • Figure 23 the essentially flat outer surface (9) of the outer tab (3) can be seen.
  • Figure 22 shows the inner surface (8) of the outer tab (3), which is also flat with the exception of the collar at the edge of the perforation (7).
  • the distance between the outer surface (9) and the inner surface (8) radially immediately outside the collar corresponds to the material thickness.
  • the material thickness of the outer plate (3) in the two embodiments of the chain according to the invention according to Figures 8 to 18 and 19 to 23 is 0.75 millimeters, as opposed to 0.80 millimeters for a burr according to the Figures 1 to 7 .
  • a step (55) is formed between the inner surface (8) around a collar (13) and the inner surface (8) at the connecting area (6) due to the recess (33). This step (55) is concentric to the hole axis (14).
  • the second outer contour (18) on the outer plate (3) corresponds to the guide side (51) of the chain joined to a chain ring. Accordingly, there is a guide chamfer (53) on the second outer contour (18) between the inner surface (8) on the connecting area (6) and the round outer contour (19) on both end areas (5) for interaction with the chain guide roller of a rear derailleur. Following the straight course of the second outer contour (18), the guide chamfer (53) also has a straight course and merges at both ends into the chamfer (34) on the round outer contour (19).
  • the first outer contour (17) on the outer plate (3) corresponds to the engagement side (50) of the chain joined to form a chain ring. Accordingly, there is a catch chamfer (16) on the first outer contour (17) between the inner surface (8) on the connecting area (6) and the round outer contour (19) on both end areas (5) for interaction with a tooth on a pinion or a chain ring .
  • the catch bevel (16) also has an arcuate shape.
  • the catching bevel (16) merges at both ends first into a transition surface and then into the bevel (34) on the round outer contour (19).
  • the formation of a transition surface corresponds to the attempt to create the smoothest possible transition and also to avoid a noticeable gap between the outer tab (3) and the adjacent inner tab (4). A gap at this point would possibly allow the tip of a sprocket tooth to penetrate, with the risk of the chain splitting open.
  • a deflecting chamfer (15) is present in a known manner between the leading side of the engagement side (50) of the outer tab (3) on the outer surface (9) of the round outer contour (19) and the outer surface (9) of the outer tab (3). There are no deflector chamfers on the guide side (51) of the outer plate (3).
  • the second embodiment of the chain plates (3, 4) shown is a further modification on the guide side (51). possible. Both the round outer contour (19) at the end regions (5) and the second outer contour (18) at the connecting region (6) can be displaced further away from the longitudinal axis (20).

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
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  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)

Claims (14)

  1. Chaîne à rouleaux pour bicyclettes comportant des plaques extérieures (3) et des plaques intérieures (4), présentant respectivement
    - une surface intérieure (8) de la plaque (3, 4) et une surface extérieure (9) de la plaque (3, 4), qui constitue également la surface extérieure de la chaîne montée ;
    - deux régions d'extrémité (5) présentant respectivement un contour extérieur circulaire (19) et une perforation cylindrique (7) disposée sensiblement concentriquement au contour extérieur circulaire (19) et dotée respectivement d'un axe de perforation géométrique (14), et
    - présentant un plan longitudinal (20) passant par l'axe de perforation (14) des perforations (7) se trouvant dans les deux régions d'extrémité (5),
    - présentant un plan transversal (21), qui constitue le plan de symétrie par rapport aux axes de perforation (14) des perforations (7) se trouvant dans les deux régions d'extrémité (5),
    - une région de liaison (6), qui relie les deux régions d'extrémité (5), comportant un premier contour extérieur (17), qui est concave, sur l'un des côtés par rapport à l'axe longitudinal (20) et comportant un deuxième contour extérieur (18) sur le côté opposé au premier contour extérieur (17) par rapport à l'axe longitudinal (20),
    - dans laquelle une première distance au bord (28) entre le premier contour extérieur (17) de la région de liaison (6) et le plan longitudinal (20) est égale à la distance au bord (27), mesurée dans une direction parallèle à l'axe transversal (21), entre le bord de la perforation (7) et le contour extérieur circulaire (19) de la région d'extrémité (5),
    dans laquelle une deuxième distance au bord (30) entre le deuxième contour extérieur (18) de la région de liaison (6) et l'axe longitudinal (20) d'au moins la moitié du rayon (29) de la perforation (7) est supérieure à la première distance au bord (28), dans laquelle le deuxième contour extérieur (18) se raccorde aux contours extérieurs circulaires (19) des deux régions d'extrémité (5) et présente une allure rectiligne, dans laquelle la deuxième distance au bord (30) est égale à un rayon de partie d'extrémité (32) des régions d'extrémité (5),
    caractérisée en ce que
    l'anneau de chaîne produit par une liaison des deux extrémités d'un morceau de chaîne l'une à l'autre présente un côté intérieur d'anneau et un côté extérieur d'anneau et le deuxième contour extérieur respectivement rectiligne (18) de la région de liaison (6) des plaques extérieures et intérieures (3, 4) est tourné vers le côté extérieur de l'anneau.
  2. Chaîne à rouleaux pour bicyclettes selon la revendication 1 comportant des tourillons de chaîne (12) et des rouleaux de chaîne (11), dans laquelle les tourillons de chaîne (12) sont reçus rotatifs dans les perforations (7) des plaques intérieures (4) et de manière bloquée en rotation dans les perforations des plaques extérieures (3) ;
    dans laquelle les plaques intérieures (4) présentent, sur leur surface intérieure, des rebords (13) sous la forme d'anneaux cylindriques, dont l'espace intérieur est respectivement concentrique à respectivement l'une des perforations (7) et présentent le même diamètre que les perforations (7) et les rouleaux de chaîne (11) sont montés rotatifs sur une paire respective de rebords opposés (13).
  3. Chaîne à rouleaux pour bicyclettes selon la revendication 1 ou 2,
    caractérisée en ce que les extrémités de tourillon (31) ne font pas saillie par rapport aux surfaces extérieures (9) des plaques extérieures (3).
  4. Chaîne à rouleaux pour bicyclettes selon l'une des revendications 1 à 3,
    caractérisée en ce que la distance, mesurée dans une direction parallèle à l'axe transversal (21), du contour extérieur circulaire (19) de la région d'extrémité (5) de la plaque intérieure (4) est supérieure au rayon du rouleau de chaîne (11), de sorte qu'une saillie transversale (26) de la plaque intérieure (4) par rapport au rouleau de chaîne (11) est formée.
  5. Chaîne à rouleaux pour bicyclettes selon l'une des revendications 1 à 3,
    caractérisée en ce que la distance, mesurée dans une direction parallèle à l'axe longitudinal (20), du contour extérieur circulaire (19) de la région d'extrémité (5) de la plaque intérieure (4) est supérieure au rayon du rouleau de chaîne (11), de sorte qu'une saillie longitudinale (25) de la plaque intérieure (4) par rapport au rouleau de chaîne (11) est formée.
  6. Chaîne à rouleaux pour bicyclettes selon la revendication 4 ou 5,
    caractérisée en ce qu'un biseau (34) est présent sur la saillie transversale (26) et/ou sur la saillie longitudinale (25).
  7. Chaîne à rouleaux pour bicyclettes selon la revendication 6,
    caractérisée en ce que l'angle de biseau (35) entre la surface intérieure (8) de la plaque intérieure (4) et le biseau (34) est de taille différente.
  8. Chaîne à rouleaux pour bicyclettes selon l'une des revendications 4 à 7,
    caractérisée en ce que l'angle de biseau (35) est de 38 degrés sur la saillie longitudinale (25) et de 51 degrés sur la saillie transversale (26).
  9. Chaîne à rouleaux pour bicyclettes selon la revendication 2 ou 3,
    caractérisée en ce que le centre du cercle du contour extérieur circulaire (19) de la région d'extrémité (5) est décalé en direction de l'axe longitudinal (20) par rapport à l'axe de perforation (14).
  10. Chaîne à rouleaux pour bicyclettes selon l'une des revendications 1 à 3,
    caractérisée en ce que l'épaisseur de matériau de la plaque intérieure (4) vaut plus de 0,7 et moins de 0,8 millimètres.
  11. Chaîne à rouleaux pour bicyclettes selon l'une des revendications 1 à 3,
    caractérisée en ce que la plaque intérieure (4) présente, dans la région de liaison (6), au niveau de la surface intérieure (8), un évidement (33), de sorte que la distance de la surface intérieure (8) à la surface extérieure (9) soit réduite en particulier à 0,6 millimètres dans la région de liaison (6).
  12. Chaîne à rouleaux pour bicyclettes selon l'une des revendications 1 à 3,
    caractérisée en ce que l'anneau de chaîne produit par une liaison des deux extrémités d'un morceau de chaîne l'une à l'autre présente un côté intérieur d'anneau et un côté extérieur d'anneau, des éléments façonnés étant présents sur les plaques intérieures (4) sur le côté tourné vers le côté extérieur d'anneau, lesquels éléments façonnés sont aptes à guider et orienter la dent, qui a pénétré à partir du côté intérieur d'anneau dans l'espace intermédiaire entre plaques (24), d'un pignon.
  13. Chaîne à rouleaux pour bicyclettes comportant des plaques extérieures (3) et des plaques intérieures (4) asymétriques par rapport à leur axe longitudinal (20), des tourillons de chaîne (12) et des rouleaux de chaîne (11), dans laquelle les tourillons de chaîne (12) sont reçus rotatifs dans les perforations (7) des plaques intérieures (4) et de manière bloquée en rotation dans les perforations (7) des plaques extérieures (3),
    dans laquelle les plaques intérieures et extérieures (3, 4) ont, sur la périphérie extérieure, sur l'un des deux côtés par rapport à l'axe longitudinal (20) passant par les centres des perforations (7), un côté d'engrènement (50) et, sur l'autre des deux côtés par rapport à l'axe longitudinal (20), un côté de guidage (51) ;
    dans laquelle les côtés d'engrènement (50) des plaques intérieures et extérieures (3, 4) présentent des biseaux de saisie (16) et des biseaux de déviation (15) pour la coopération avec les dents sur les pignons arrière et avant, et
    dans laquelle les côtés de guidage (51) des plaques intérieures et extérieures (3, 4) présentent des biseaux de guidage (53), de sorte que la chaîne à rouleaux, lors du contact avec le rouleau de guidage de chaîne (52) d'un dérailleur arrière, soit guidée par le rouleau de guidage de chaîne (52),
    caractérisée en ce que la périphérie extérieure des plaques intérieures et extérieures (3, 4) sur le côté de guidage (51) de la chaîne présente une allure rectiligne.
  14. Chaîne à rouleaux pour bicyclettes selon la revendication 13,
    caractérisée en ce que le côté de guidage (51) de la chaîne est disposé au niveau d'un côté extérieur d'un anneau de chaîne.
EP17001781.8A 2016-11-03 2017-10-27 Chaînes à rouleau pour cycle Active EP3318335B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016013112 2016-11-03
DE102017009632.5A DE102017009632A1 (de) 2016-11-03 2017-10-16 Rollenketten für Fahrräder

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EP3318335A1 EP3318335A1 (fr) 2018-05-09
EP3318335A8 EP3318335A8 (fr) 2018-07-18
EP3318335B1 true EP3318335B1 (fr) 2023-11-29

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CN (1) CN108019461B (fr)
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DE102018207361A1 (de) 2018-05-11 2019-11-14 Sram Deutschland Gmbh Asymmetrische Fahrradketten-Innenlasche, Fahrradketten-Außenlasche und Fahrradkette mit wenigstens einer derartigen Lasche
EP3636535B1 (fr) * 2018-10-09 2023-08-02 Miranda & Irmão Lda. Système de chaîne d'entraînement
TWI747152B (zh) * 2019-02-05 2021-11-21 美商速聯有限責任公司 用於自行車的驅動配置
US11767078B2 (en) 2019-02-05 2023-09-26 Sram Deutschland Gmbh Drive arrangement for a bicycle
DE102020211481A1 (de) * 2019-10-08 2021-04-08 Sram Deutschland Gmbh Fahrradkette mit partiell reduzierter aussenkontur der innenlasche

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE93477C (de) * 1896-12-30 1897-08-18 Frederick William Barker Treibkette fur fahrrader
GB2000846A (en) * 1977-07-06 1979-01-17 Sedis Transmissions Mec Transmission chain

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1285011B1 (it) * 1996-03-18 1998-06-03 Campagnolo Srl Catena di trasmissione, particolarmente per bicicletta.
DE102004011572A1 (de) * 2004-03-10 2005-09-29 Sram Deutschland Gmbh Fahrradkette mit ausgebauchten Außen- und außen angefasten Innenlaschen
DE102006005157A1 (de) * 2006-02-04 2007-08-23 Sram Deutschland Gmbh Ketten-Verschlussglied
US8734280B2 (en) * 2011-06-15 2014-05-27 Shimano Inc. Inner link plate for bicycle chain
DE202013011442U1 (de) * 2013-12-20 2014-01-23 Sram Deutschland Gmbh Kettenrad
JP5975139B1 (ja) * 2015-04-21 2016-08-23 アールケー・ジャパン株式会社 異形プレートチェーン

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE93477C (de) * 1896-12-30 1897-08-18 Frederick William Barker Treibkette fur fahrrader
GB2000846A (en) * 1977-07-06 1979-01-17 Sedis Transmissions Mec Transmission chain

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
"JIS D 9417:2004 Bicycles-Chains (English Version)", JIS JAPANESE INDUSTRIAL STANDARD, JAPANESE STANDARDS ASSOCIATION, vol. D 9417, 1 September 2004 (2004-09-01), XP009520190 *

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TWI750251B (zh) 2021-12-21
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EP3318335A8 (fr) 2018-07-18
EP3318335A1 (fr) 2018-05-09
CN108019461A (zh) 2018-05-11

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